EP3443131B1 - Blaslanzendüse - Google Patents

Blaslanzendüse Download PDF

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Publication number
EP3443131B1
EP3443131B1 EP17719524.5A EP17719524A EP3443131B1 EP 3443131 B1 EP3443131 B1 EP 3443131B1 EP 17719524 A EP17719524 A EP 17719524A EP 3443131 B1 EP3443131 B1 EP 3443131B1
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EP
European Patent Office
Prior art keywords
front wall
separator
bath
advantageously
pillar
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EP17719524.5A
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English (en)
French (fr)
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EP3443131A1 (de
Inventor
Jean-Philippe Thomas
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Soudobeam SA
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Soudobeam SA
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Priority to PL17719524T priority Critical patent/PL3443131T3/pl
Publication of EP3443131A1 publication Critical patent/EP3443131A1/de
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    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21C—PROCESSING OF PIG-IRON, e.g. REFINING, MANUFACTURE OF WROUGHT-IRON OR STEEL; TREATMENT IN MOLTEN STATE OF FERROUS ALLOYS
    • C21C5/00—Manufacture of carbon-steel, e.g. plain mild steel, medium carbon steel or cast steel or stainless steel
    • C21C5/28—Manufacture of steel in the converter
    • C21C5/42—Constructional features of converters
    • C21C5/46—Details or accessories
    • C21C5/4606—Lances or injectors
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21C—PROCESSING OF PIG-IRON, e.g. REFINING, MANUFACTURE OF WROUGHT-IRON OR STEEL; TREATMENT IN MOLTEN STATE OF FERROUS ALLOYS
    • C21C5/00—Manufacture of carbon-steel, e.g. plain mild steel, medium carbon steel or cast steel or stainless steel
    • C21C5/28—Manufacture of steel in the converter
    • C21C5/42—Constructional features of converters
    • C21C5/46—Details or accessories
    • C21C5/4606—Lances or injectors
    • C21C2005/4626—Means for cooling, e.g. by gases, fluids or liquids

Definitions

  • the blowing lance nose as described in the present invention is used, inter alia, in oxygen converters for the manufacture of steel (BOF Basic Oxygen Furnace, AOD Argon Oxygen Decarburization). Converters make it possible to obtain steel by injecting oxygen into a liquid iron bath in order to burn the carbon contained therein.
  • the basic principle in the field of oxygen blowing in converters (for example LD (for Linz-Donawitz)) is to propel 3 to 6 jets of oxygen arranged in a crown on a bath of liquid cast iron. The lance which allows the formation of these oxygen jets is then placed at a distance of 1 to 5 m above a bath of molten iron whose temperature can reach 1700 ° C.
  • the temperature of the nose of the lance can then increase rapidly to 400 ° C. and must remain in this environment for approximately 20 minutes.
  • the nose is then removed and returns to room temperature, that is to say 20 ° C.
  • the document EP0340207 provides for a significant depression in the central area of the lance nose on which are directed secondary jets of coolant causing a swirl in the flow of the liquid.
  • the document WO0222892 attempts to further improve the flow of coolant in the heat exchange space of the lance nose by developing a central depression in the face facing the bath having a well determined ratio between height and base of this depression. This ratio allows the heat exchange space to have a section for the passage of the coolant substantially constant so as to obtain a speed of passage of the coolant through this space which is approximately constant.
  • the document DE 19506718 describes a blowing lance nose used in or above liquid steel and having a cooling system based on the difference in roughness between the two walls of the heat exchange space, namely the separator and the internal surface of the third front wall.
  • the ratio of the difference in roughness to the minimum radius of curvature of the surface exposed to the liquid steel must be kept constant to ensure good cooling.
  • US2012 / 0211929 A1 discloses another example of the known prior art relating to a blowing lance nose.
  • the diameter of the outlet openings of the injectors tends to increase following the erosion of the edges thereof. This increase in diameter deforms the oxygen jets, which causes, in addition to the destruction of the lance nose, a dispersion of these jets and consequently a reduction in their effectiveness.
  • the carbon oxidation reaction is, in fact, favored by the depth of penetration of the jets into the bath and by the mixing thereof.
  • the lance noses being placed at a distance of 1 to 5 m above the cast iron bath, in order to be effective, the jets must have a coherent profile over the longest possible distance. The reaction yield is then reduced when these jets are dispersed because they penetrate less deeply into the melt. The reaction yield in the bath is therefore not optimal and moreover exhibits significant variability during the lifetime of the lance nose.
  • Efficient cooling is therefore important for the proper functioning of the lance noses, since it has the advantage of increasing the lifetime of the latter but also of guaranteeing better stability of reaction yield throughout their lifetime. and this by minimizing erosion at the edges of the front wall.
  • such cooling is also very difficult to implement, under the extreme conditions encountered during the use of the lance noses.
  • the object of the present invention is to overcome these drawbacks of the state of the art by providing a lance nose which is simple to manufacture, the lifetime of which is increased and which makes it possible to ensure a reaction yield in the improved cast iron bath and stable throughout the life of the lance nose.
  • a lance nose as indicated at the beginning in which the separator has at the central opening an edge in axial section which is curved such that a height H3 is defined between a front of said edge and said internal surface of the third front wall and that in the heat exchange space a predetermined minimum height H1 is present on the side of said central opening such that the ratio H1 / H3 is between 5% and 80 %, advantageously between 5% and 75%, preferably between 5% and 70%, preferably between 5% and 65%, particularly advantageously between 5% and 60%, preferably between 10% and 60% , advantageously between 15% and 60%, preferably between 20% and 60%, preferably between 25% and 60%, particularly advantageously between 25% and 55%, preferably between 30% and 55%.
  • the edge of the separator at the central opening thanks to its curved axial section, allows the coolant, arriving from the first annular cavity, to carry out a progressive rotation between this curved edge and the central depression of the internal surface of the third front wall to arrive without disturbance in the heat exchange space.
  • the injectors in the lance nose represent obstacles which are in the path of the coolant, first between the first and the second front wall and then in the heat exchange space between the second and the third wall frontal. It is therefore necessary to "calm" the coolant after bypassing the first obstacle which are the injectors between the first and the second front wall.
  • This role is achieved according to the present invention by the edge of the separator which is curved in axial section and which makes it possible to form at the central opening and in the heat exchange space passage sections for the coolant optimized.
  • this curved edge in axial section of the separator makes it possible to minimize the energy losses in the flow of the coolant which improves the acceleration of this liquid during its passage between the curved edge of the separator and the conical central zone. of the internal surface of the third front wall, before it arrives in the heat exchange space.
  • This first acceleration is regulated by the section of the coolant passage between the edge of the separator and the central depression.
  • H1 is the height minimal passage of water along the internal surface of the third front wall, in the heat exchange space. This first acceleration improves the cooling of the central part of the lance nose which is the part where the metal / liquid exchange surface is the least important and therefore the most difficult area to cool.
  • passage section is meant, according to the present invention, a section taken perpendicular to the direction of flow of the coolant.
  • the positioning of the separator relative to the third front wall makes it possible to form a heat exchange space having a predetermined height which regulates the acceleration of the coolant.
  • the separator according to the present invention is substantially planar and substantially parallel to the third front wall thus ensuring a flow of the coolant with turbulence and reduced cavitation phenomenon.
  • the lance nose according to the present invention therefore makes it possible both to optimize the trajectory of the coolant, which minimizes turbulence, and to improve the acceleration of this liquid to effectively cool the wall exposed to thermal stresses. Consequently, the life of the lance nose according to the present invention is considerably increased and the erosion of the outlet edges of the injectors is minimized so that the reaction yield in the bath is improved and kept stable throughout the life of the lance nose. Indeed, good cooling reduces erosion of the outlet edges for the stirring gas, which makes it possible to obtain more coherent jets at the outlet of the injectors. These more coherent jets penetrate deeper into the cast iron bath and ensure better stirring thereof, thereby ensuring an improvement in the yield of the reaction in the bath.
  • the gases and dusts emitted on the surface of the bath and going up towards the lance nose less impact the degradation of the nose when the cooling of this one is improved as for the nose of the present invention.
  • the life of the nose according to the present invention is increased.
  • the lance nose according to the present invention has a predetermined outer diameter D ext and said edge of the separator is defined by a thickness e1 so that the ratio e1 / D ext is between 3% and 30%, preferably between 4% and 25%, advantageously between 5% and 20%, preferably between 5% and 15%.
  • the thickness, e1 of the edge of the separator is the distance, taken parallel to the axis of revolution of the injectors, between the surface facing the first front wall and the surface facing the bath of the separator.
  • This particular thickness of the edge of the separator allows on the one hand to further improve the rotation of the coolant around the edge of the separator which faces the central depression.
  • the particular thickness of the edge of the separator advantageously reduces the energy losses during the flow of the coolant. The reduction in energy losses in turn leads to maintaining the acceleration of the liquid and therefore to optimizing the cooling of the nose.
  • the separator of the lance nose has a surface, facing the bath, substantially sinusoidal.
  • sinusoidal surface is meant a surface which forms a wavy curve, that is to say which has for example a convex part between two concave parts.
  • the separator having a sinusoidal surface therefore has a convex part between two concave parts with respect to the third front wall. A minimum thickness is therefore located between two maximum thicknesses of the separator.
  • This sinusoidal surface has the advantage of offering the coolant a passage section in the improved heat exchange space. Indeed, as mentioned above, a first Acceleration of the coolant occurs before entering the heat exchange space.
  • the sinusoidal surface of the separator has the effect of increasing the cross section of the coolant substantially in the center of the separator. Indeed, the injectors which pass through the separator substantially at its center, clutter the heat exchange space. This is where the separator is made concave (has an inward bulge) to leave room for the passage of coolant.
  • the sinusoidal shape of the surface facing the separator bath therefore makes it possible to reduce the energy losses during the second bypass of the injectors between the separator and the internal surface of the third front wall. This sinusoidal surface is advantageous for the good cooling of the wall exposed to the liquid iron bath.
  • said surface facing the substantially sinusoidal bath of said separator is such that the heat exchange space has a maximum height substantially at the center of said separator.
  • the lance nose according to the invention has a pillar comprising a first end situated opposite the bath and a second end facing the bath connected to the central zone of the third front wall.
  • This pillar allows on the one hand to improve the circulation of the coolant when it plunges into the central opening.
  • the central opening can be a place of collision and the pillar present at the center of this central opening therefore makes it possible to minimize turbulence.
  • the liquid will then go along the pillar before arriving in the heat exchange space.
  • this pillar advantageously made of a material with good thermal conductivity, such as copper, makes it possible to ensure a good transfer of the calories accumulated in the front wall exposed to the bath to the coolant. This phenomenon of calorie transfer is called "cold well". The heat transferred by the pillar then diffuses towards the coolant circulating around it.
  • the pillar has between said first and second ends a thinned part connected to the central zone which has a predetermined length L1 and an axial section continuously decreasing towards the central zone so that the pillar forms with the central zone from the internal surface of the third front wall a continuous curved surface.
  • continuous curved surface is meant a surface which has a “continuity of curves”, preferably a “continuity of tangents”.
  • continuous of tangents is meant, according to the present invention, that, in an axial section of the pillar, the curve of the thinned part of the pillar and the curve of the conical central zone of the internal surface of the third front wall have equal tangents at their common end, that is to say at their junction (second end of the pillar). Tangents are the first derivatives of curves at their common end.
  • a second degree of “continuity of curves” can possibly be a “continuity of curvatures”, which then means that the radii of curvature of the two curves (thinned part of the pillar and of the conical central zone of the internal surface of the third wall frontal) are equal at their common end, that is to say at their junction (second end of the pillar).
  • the curves of the thinned part of the pillar and of the conical central zone of the internal surface of the third front wall have the same direction at their junction and also have the same radius at this point.
  • the radii of curvature are the second derivatives of the curves at their common end, that is to say at their junction at the second end of the pillar.
  • the coolant arriving from the peripheral part of the nose converges in the central opening where it performs a rotation of approximately 180 ° between the pillar and the edge of the separator before arriving in the exchange space thermal, for example frontal.
  • This pillar having a particular geometry allows, on the one hand, to further optimize the flow of coolant passing through the central opening where it passes between the thinned part of the pillar and the edge of the separator and on the other part of accelerating the coolant before it arrives in the heat exchange space.
  • the edge of the separator according to the present invention has a complementary shape with the thinned part of the central pillar advantageously present in the center of the central opening.
  • This complementary shape between these two elements is particularly advantageous for accompanying the coolant during its rotation of about 180 ° in the central opening, thus making it possible to lessen the turbulence in the liquid, to “calm it down”, and maintain good contact with the pillar serving as a "cold well” and then with the third front wall. Furthermore, this geometry also allows the acceleration of the coolant before it passes through the heat exchange space.
  • the pillar has a second part of predetermined length L2 joining said thinned part and said first end, said second part having a circular cross section defined by a predetermined diameter D2, constant over the entire length L2 such that the ratio D2 / D ext , is between 2% and 30%, advantageously between 7.5% and 17.5%, preferably between 10% and 15% of said outside diameter (D ext ) of the nose of launch.
  • the pillar can be considered as “massive” in view of the volume it occupies in the nose.
  • This massive pillar made of a material with good thermal conductivity, such as copper, ensures good transfer of calories accumulated in the front wall exposed to the bath to the coolant, thus improving the phenomenon of "cold well".
  • the heat transferred by the pillar then diffuses towards the coolant circulating around it and whose metal / liquid heat exchange surface is increased thanks to the thinned part having a curved profile.
  • the heat is, therefore, better distributed within the lance nose which more particularly ensures good cooling of the area most exposed to extreme temperatures, namely the center of the third front wall.
  • the lance nose according to this embodiment therefore results in an additional improvement in the cooling of the nose.
  • said thinned part I of the pillar has a predetermined minimum diameter D3 at its second end and said central zone has a height h and a base b such that the ratio h / (b-D3) is between 20% and 120%, preferably between 20% and 110%, advantageously between 30% and 110%, preferably between 30% and 100%, in particular between 40% and 100%, particularly advantageously between 40% and 90%, preferably between 45% and 85%, advantageously between 50% and 80%.
  • the heat exchange surface is thus increased relative to the same surface of the heat front coming from the bath, and this without causing either swirling or cavitation in the liquid.
  • the cross section of the liquid in the heat exchange space is such that the coolant has an adequate speed profile so that the cooling of the front wall exposed to the bath is further improved.
  • the lance nose according to the present invention is characterized by a distance R, for the passage of the coolant, taken perpendicular to the longitudinal axis L of the nose in the central opening.
  • this passage distance is then called R 1 and is measured between the front of the separator and the longitudinal axis of the nose, and therefore corresponds to the minimum radius of the central opening .
  • R 1 the passage distance for the liquid is then measured between the front of the separator and the external surface of the thinned part I of the pillar, the distance is then called R 2 .
  • this passage distance R is such that the ratio R / H3 is between 20% and 150%, preferably between 30% and 140%, advantageously between 30% and 130%, preferably between 40% and 130%, particularly advantageously between 50% and 130%, preferably between 60% and 120%, advantageously between 60% and 110%, reference between 70% and 110%, with R corresponding to R1 in the absence pillar or corresponding to R2 in the presence of a pillar.
  • This particular passage distance for the coolant makes it possible to further improve the flow of the coolant which will converge in the central opening before reaching the heat exchange space.
  • the distance of passage of the liquid in the central opening in combination with the characteristics of the aforementioned nose makes it possible to further improve the flow by improving the reduction of the disturbances and the acceleration of the coolant.
  • said separator has a surface facing said first substantially sinusoidal front wall.
  • a deflector is present substantially in the center of said central tube for supplying stirring gas to the lance nose according to the present invention.
  • This deflector makes it possible to appropriately divert the gas leaving the central duct to engage in the outlet conduits for the stirring gas.
  • said outlet conduits for the gas stirring have axes of revolution placed obliquely to a longitudinal axis of the lance nose.
  • the aforementioned elements of the nose are produced separately and fixed in the area of mutual connection by high energy welding, preferably an electron beam welding.
  • the aforementioned nose is made of several nose elements each consisting of a material chosen according to the function to be fulfilled. These elements are then fixed together by high energy welding, preferably by electron beam. This type of welding provides easily achievable copper-steel junctions with good liquid tightness, despite the fatigue stresses due to the successive thermal cycles to which the nose is subjected.
  • the figure 1 illustrates the third front wall 12 of the lance nose 1 which faces the bath.
  • the lance nose 1 has six brewing gas outlet orifices 13 placed in a ring around a central zone 14 of the third front wall 12.
  • the figure 2 represents the lance nose according to the present invention in which the stirring gas is supplied by the central tube 2.
  • This central tube 2 is closed by a front wall 3 directed towards the bath provided with at least two openings 4.
  • An internal tube 5 is arranged coaxially around the central tube 2 so as to form between them an annular cavity 6 serving for the supply of coolant in the direction of the arrow F 1 .
  • This internal tube 5 is terminated by a front wall 7 which is called a separator.
  • This front wall 7 is provided with a central opening 8 and an orifice 9 in alignment with each opening 4 in the central tube 2.
  • the separator 7, according to the present invention, has a geometry and an arrangement relative to the third particular front wall 12 which will be developed below.
  • An external tube 10 is arranged coaxially around the internal tube 5.
  • This external tube forms with the internal tube 5 an annular cavity 11 which serves for the outlet of the coolant in the direction of the arrow F 2 .
  • This external tube is closed by a front wall 12 which faces the brewing bath and which has an internal surface 30.
  • the internal surface 30 of the third front wall 12 is provided with a conical central zone 14 which is directed towards the central opening 8 and which has a surface of a curved envelope in axial section.
  • the front wall 12 is also provided with an outlet orifice 13 in alignment with each opening 4 provided in the front wall 3 and with each passage orifice 9 provided in the front wall 7.
  • an outlet conduit 17 for the ejection of stirring gas outside the lance nose.
  • the axes of revolution m of the conduits 17 are advantageously placed obliquely to the longitudinal axis L of the lance nose.
  • this front wall 12 is ensured by the circulation of the cooling liquid in the heat exchange space 16 which is located between the separator 7 and the internal surface 30 of the front wall 12.
  • the coolant coming from the cavity 6 passes through the central opening 8 in the heat exchange zone 16 according to the arrow F 3 .
  • the liquid then flows in the direction of arrow F 2 towards the outside, that is to say towards the cavity 11.
  • the separator 7, according to the present invention is substantially planar and substantially parallel to the internal surface 30 of the third front wall 12.
  • This separator 7 has, at the central opening 8, an edge 18 of curved axial section.
  • a minimum diameter of the central opening 8 can then be measured from the front 19 of the edge 18 of the separator 7.
  • the tangent passing through this front 19 and parallel to the longitudinal axis L of the lance nose makes it possible to measure the diameter the smallest of the central opening 8.
  • the height taken along the tangent passing through the front 19 and parallel to the longitudinal axis L of the lance nose and measured between said front 19 and the internal surface 30 of the third front wall 12 corresponds to the height H3, such that 'indicated on the figure 3 .
  • the height H1 is in turn measured, parallel to the axis of revolution m of the injectors 17, between the surface facing the bath 20 of the separator 7 and the internal surface 30 of the third front wall 12, on the side of the opening central 8.
  • This height H1 defines a minimum passage height for the coolant in the heat exchange space 16 at the central opening 8.
  • H1 is the minimum height of the passage of water along the internal surface of the third front wall, in space heat exchange. According to the present invention, the H 1 / H 3 ratio is advantageously between 30% and 55%.
  • the curved axial section of the edge 18 of the separator 7 has the advantage of accompanying the coolant when it converges in the central opening 8.
  • the coolant thus "tranquilized” can then calmly bypass the obstacles represented by the injectors 17 in the heat exchange space 16 before emerging from the nose through the second annular cavity 11 along the arrow F 2 .
  • the external diameter D ext of the lance nose 1 according to the present invention corresponds to the diameter measured between the external surfaces of the external tube 10, as shown in the figure 2 .
  • a thickness of the separator 7 is measured between the surface 21 facing the first front wall 3 and the surface facing the bath 20 of the separator 7.
  • the thickness e1 of the edge 18 of the separator 7 is therefore measured parallel to the axis of revolution m of the injector 17 in continuity with the minimum height H1 of the heat exchange space 16 at the central opening 8.
  • This thickness allows the separator to occupy a substantial volume in the lance nose and allows in combination with the curved section of the edge 18 to maintain a flow with reduced disturbance and good acceleration of the coolant.
  • the ratio e1 / D ext is between 5% and 15%
  • the surface facing the bath 20 of the separator 7 is substantially sinusoidal.
  • the maximum thickness, e1 is measured between the surface 21 facing the first front wall 3 and the tangent passing through the minimum of the part concave of the surface facing the bath 20.
  • a minimum thickness is measured between the surface 21 facing the first front wall 3 and the tangent passing through the maximum of the convex part of the surface facing the bath 20.
  • the separator 7 has, in addition to its thickness e1 at the central opening 8, a minimum thickness substantially at its center such that the heat exchange space 16 has a maximum height H max substantially at the center of the separator 7.
  • This height maximum H max is intended to leave more space for the coolant when it passes through the injectors 17 in the heat exchange space 16.
  • the figure 4 represents a particular embodiment of the lance nose according to the present invention.
  • a central pillar 22 of particular configuration is present at the center of the central opening 8.
  • the pillar 22 has a first end E1 on the side of the first front wall 3 and a second end E2 connected to the central zone 14 of the internal surface 30 of the third front wall 12.
  • This pillar preferably has a thinned part I between the first end E1 and the second end E2 which makes it possible to form a continuous curved surface 23 with the conical central zone 14 of the internal surface 30 of the third front wall 12.
  • the coolant coming from the first cavity annular 6 along arrow F 1 runs along the upper face 21 of the separator 7 where it must bypass the injectors which represent a first obstacle on the trajectory of the liquid and then converges in the central opening 8.
  • the pillar 22 present at the center of this central opening 8 then makes it possible to guide the coolant towards the internal surface 30 of the third front wall 12 where the thinned part I of the pillar ensures the passage of the liquid between this pillar 22 and the edge 18 of the separator 7, along the arrow F 3 .
  • the junction of the conical central zone 14 of the internal surface 30 of the third front wall 12 with the pillar 22 has a continuous curved surface 23 ensuring a progressive rotation of the liquid according to arrow F 3 .
  • the turbulence in the coolant then arriving in the heat exchange space 16 is reduced and the liquid can quietly bypass the injectors occupying a large volume in the heat exchange space 16.
  • the calories accumulated in the front wall 12 exposed to the liquid iron bath are transferred to the pillar 22 whose contact surface with the coolant is increased thanks to its thinned part I, which improves the metal / liquid heat transfer
  • the pillar 22 advantageously has a second part II of predetermined length L2 joining said thinned part I and said first end E1, said second part II having a circular cross section defined by a predetermined diameter D2, constant over the entire length L2 , such that the ratio D2 / D ext is advantageously between 10% and 15%.
  • the pillar 22 being made of a material of good thermal conductivity, the heat coming from the bath and transmitted to the third front wall 12 and to its central zone 14 where it can then be led by the pillar 22 to the coolant. .
  • the latter circulating around the pillar 22 ensures constant capture of the heat from the third front wall 12.
  • the parts most exposed to the bath namely the third front wall 12 and the pillar 22, are made of wrought copper which provides better thermal conductivity than cast copper.
  • the first thinned part I is further characterized by a predetermined diameter D1 which varies progressively from the diameter D2 at the junction with the second part II to a value preferably between 60% and 80% of D2 at the second end E2 of the pillar 22.
  • the diameter D1 of the thinned part I of the pillar 22 therefore gradually decreases when one moves along the longitudinal axis L of the lance nose towards the bath until reaching a minimum value, then called D3 corresponding to the second end E2 of the pillar.
  • the continuous curved surface 23 between the thinned part I of the pillar 22 and the conical central zone 14 of the internal surface 30 of the third front wall 12 is characterized by a radius of curvature greater than or equal to 30% of the diameter D2 of the second part II of pillar 22.
  • the separator 7 and the thinned part I of the pillar 22 facing each other have a complementary shape thus ensuring the most delicate possible coolant support.
  • the edge 18 of the separator 7 and the thinned part I of the pillar 22 make it possible to form for the coolant a trajectory reducing the turbulence in the liquid.
  • a deflector 24 can also be placed in the center of the stirring gas supply tube 2. This deflector 24 makes it possible to appropriately divert the oxygen leaving the central pipe 2 to engage in the injectors 17.
  • the figure 5 represents a detail of the conical central zone 14 in order to explain how to measure the parameters relating to this central zone 14 of the internal surface 30 of the third front wall 12.
  • the height h is measured between the tangent plane 32 of the wall internal 30 of the lance nose perpendicular to the longitudinal axis L and the parallel plane 31 tangent to the apex of the conical central zone 14. If an additional element to the conical central zone 14 is provided at the apex thereof, as for example pillar 22, plan 31 remains in the position it would have if this additional element did not exist.
  • the apex of the conical central zone 14 coinciding with the cross section of the thinned part I of the pillar 18 having a minimum diameter D3, the plane 31 also passes through this section of minimum diameter D3 of the pillar 22.
  • the base b is situated in the tangent plane 32 of the internal wall 30. It is circumscribed by the points of intersection 33 with the extension of the internal wall 30.
  • the nose according to the present invention has an h / (b-D3) ratio of between 50% and 80%. Therefore, in the case where no additional element, such as for example a pillar, is present on the central zone 14, D3 is zero and the h / b ratio is preferably between 50% and 80%.
  • the figure 5 also represents the distance R for the passage of the coolant taken perpendicular to the longitudinal axis L of the nose in the central opening 8.
  • the distance R is measured between the front 19 of the separator 7 and the longitudinal axis L, this distance for the passage of the coolant is then called R 1 and corresponds to the minimum radius of the central opening 8.
  • the passage distance R for the liquid is then measured between the separating front 19 and the external surface of the thinned part I of the pillar 22, the distance is then called R 2 .
  • this distance for the passage of the coolant is such that the ratio R / H3 is preferably between 70% and 110%, with R corresponding to R1 in the absence of a pillar or corresponding to R2 in the presence of a pillar.

Claims (10)

  1. Blaslanzendüse (1), die zum Rühren einer Schmelze bestimmt ist, Folgendes umfassend:
    - ein zentrales Rohr zur Versorgung mit Rührgas (2), das an einem Ende, das der Schmelze zugewandt ist, durch eine erste Vorderwand (3) geschlossen ist, die mit mindestens zwei Öffnungen (4) versehen ist,
    - ein inneres Rohr (5), das mit dem zentralen Rohr (2) einen ersten ringförmigen Hohlraum (6) für den Durchgang einer Kühlflüssigkeit bildet, und an einem Ende, das der Schmelze zugewandt ist, durch eine zweite, Separator (7) genannte, Vorderwand abgeschlossen ist, die eine zentrale Öffnung (8) und ein Durchgangsloch (9) durch eine Öffnung, die in der ersten Vorderwand (4) vorgesehen ist, aufweist,
    - ein äußeres Rohr (10), das mit dem inneren Rohr (5) einen zweiten ringförmigen Hohlraum (11) für den Durchgang der Kühlflüssigkeit bildet, und an einem Ende, das der Schmelze zugewandt ist, durch eine dritte Vorderwand (12) geschlossen ist, die ein Ausgangsloch (13) durch eine Öffnung aufweist, die in der ersten Vorderwand (4) vorgesehen ist, und eine innere Oberfläche (30) aufweist, die eine konische zentrale Zone (14) umfasst, die zur zentralen Öffnung (8) gerichtet ist, und die eine im axialen Querschnitt gebogene Hüllenoberfläche aufweist,
    - einen Wärmetauschraum (16) in dem die Kühlflüssigkeit strömt, der sich zwischen einerseits dem Separator (7) und der dritten Vorderwand (12), und andererseits der zentralen Öffnung (8) und dem zweiten ringförmigen Hohlraum (11) befindet, und in dem die Kühlflüssigkeit strömt, und
    - eine Ausgangsleitung für das Rührgas, Inj ektor (17) genannt, die von j eder Öffnung (4) in der ersten Vorderwand (3) abgeht, und bis zu einem entsprechenden zuvor genannten Ausgangsloch (13) verläuft, in einer gegenüber der Kühlflüssigkeit dichten Art und Weise durch ein entsprechendes zuvor genanntes Durchgangsloch (9) führend,
    dadurch gekennzeichnet, dass der Separator (7) an der zentralen Öffnung (8) im axialen Querschnitt einen Rand (18) aufweist, der derart gebogen ist, dass (H3) zwischen einer Stirnseite (19) des Randes (18) und der dritten Vorderwand (12) eine Höhe definiert wird, und dass in dem Wärmetauschraum (16) eine vorbestimmte Mindesthöhe (H1) auf Seiten der zentralen Öffnung (8) vorhanden ist, sodass das Verhältnis H1/H3 zwischen 5% und 80% enthalten ist, vorteilshalber zwischen 5% und 75%, vorzugsweise zwischen 5% und 70% enthalten ist, auf bevorzugte Weise zwischen 5% und 65% enthalten ist, und ganz besonders vorteilhaft zwischen 5% und 60%, vorzugsweise zwischen 10% und 60%, vorteilshalber zwischen 15% und 60%, und vorzugsweise zwischen 20% und 60% enthalten ist, auf bevorzugte Weise zwischen 25% und 60% enthalten ist, auf ganz besonders bevorzugte Weise zwischen 25% und 55% enthalten ist, vorzugsweise zwischen 30% und 55% enthalten ist.
  2. Lanzendüse nach Anspruch 1, durch eine Distanz R für den Durchgang der Kühlflüssigkeit gekennzeichnet, die senkrecht zur Längsachse L der Düse zwischen der Stirnseite (19) des Randes (18) des Separators (7) und der Längsachse L der Düse genommen wird, wobei die Distanz R derart ist, dass das Verhältnis R/H3 zwischen 20% und 150% enthalten ist, vorzugsweise zwischen 30% und 140%, vorteilhafter Weise zwischen 30% und 130%, auf bevorzugte Weise zwischen 40% und 130%, auf besonders vorteilhafte Weise zwischen 50% und 130%, vorzugsweise zwischen 60% und 120%, vorteilhafterweise zwischen 60% und 110%, vorzugsweise zwischen 70% und 110% enthalten ist.
  3. Lanzendüse nach einem der Ansprüche 1 und 2, einen vorbestimmten Außendurchmesser (Dext) aufweisend, und in der der Rand (18) des Separators (7) durch eine Dicke (e1) definiert ist, sodass das Verhältnis e1/ Dext zwischen 5% und 30% enthalten ist, vorzugsweise zwischen 7% und 25% enthalten ist, vorteilshalber zwischen 7% und 20%, auf bevorzugte Weise zwischen 7% und 15% enthalten ist.
  4. Lanzendüse nach einem der Ansprüche 1 bis 3, wobei der Separator (7) eine im Wesentlichen sinusförmige Oberfläche aufweist, die der Schmelze (20) zugewandt ist.
  5. Lanzendüse nach einem der Ansprüche 1 bis 4, eine Säule (22) aufweisend, die ein erstes Ende (E1) umfasst, das sich entgegengesetzt zur Schmelze befindet, und ein zweites Ende (E2), das der Schmelze zugewandt ist, mit einer zentralen Zone (14) der inneren Oberfläche (30) der dritten Vorderwand (12) verbunden.
  6. Lanzendüse nach Anspruch 5, wobei die Säule (22) zwischen dem ersten und zweiten Ende (E1 und E2) ein verjüngtes Teil (I) aufweist, das mit der zentralen Zone (14) verbunden ist, die eine vorbestimmte Länge L1 und einen abnehmenden axialen Querschnitt aufweist, sodass die Säule (18) mit der zentralen Zone (14) der inneren Oberfläche (30) der dritten Vorderwand (12) eine durchgehende gebogene Oberfläche (23) bildet.
  7. Lanzendüse nach einem der Ansprüche 1 bis 6, wobei der verjüngte Teil I der Säule (22) einen vorbestimmten Mindestdurchmesser D3 an dem zweiten Ende (E2) aufweist, und die zentrale Zone (14) der inneren Oberfläche (30) der dritten Vorderwand (12) eine Höhe h und eine Basis b aufweist, sodass das Verhältnis h/ (b-D3) zwischen 20% und 120%, vorzugsweise zwischen 20% und 110%, vorteilshalber zwischen 30% und 110%, in bevorzugter Weise zwischen 30% und 100%, insbesondere zwischen 40% und 100% enthalten ist, auf besonders bevorzugte Weise zwischen 40% und 90%, vorzugsweise zwischen 45% und 85%, vorteilshalber zwischen 50% und 80% enthalten ist.
  8. Lanzendüse nach einem der Ansprüche 1 bis 7, wobei ein Abweiser (24) im Wesentlichen im Zentrum des zentralen Rohres zur Versorgung mit Rührgas (2) vorhanden ist.
  9. Lanzendüse nach einem der Ansprüche 1 bis 8, wobei die Injektoren (17) eine Drehachse (m) aufweisen, die im Verhältnis zu einer Längsachse (L) der Lanzendüse schräg ausgerichtet ist.
  10. Blaslanzendüse nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass die Elemente der Düse getrennt gefertigt werden und in einer gegenseitigen Montagezone durch Hochenergieschweißen, vorzugsweise durch Elektronenstrahlschweißen befestigt werden.
EP17719524.5A 2016-04-15 2017-04-13 Blaslanzendüse Active EP3443131B1 (de)

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BE2016/5263A BE1023609B1 (fr) 2016-04-15 2016-04-15 Nez de lance de soufflage
PCT/EP2017/058973 WO2017178606A1 (fr) 2016-04-15 2017-04-13 Nez de lance de soufflage

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FR2521167B1 (fr) 1982-02-10 1987-04-30 Siderurgie Fse Inst Rech Lance d'injection de gaz pour convertisseur metallurgique
AT389710B (de) 1988-04-25 1990-01-25 Voest Alpine Ind Anlagen Blaslanze
RU2051974C1 (ru) 1995-01-25 1996-01-10 Александр Леонидович Кузьмин Наконечник кислородно-конвертерной фурмы
DE19506718A1 (de) * 1995-02-27 1996-08-29 Eko Stahl Gmbh Lanzenkopf für eine wassergekühlte Blaslanze
BE1009743A3 (fr) * 1995-06-23 1997-07-01 Thomas Jacques Tuyere de soufflage a oxygene siderurgique.
US6217824B1 (en) * 1999-05-20 2001-04-17 Berry Metal Company Combined forged and cast lance tip assembly
BE1013686A3 (fr) * 2000-09-15 2002-06-04 Thomas Jacques Nez de lance de soufflage.
US7402274B2 (en) * 2005-12-07 2008-07-22 Berry Metal Company Metal making lance slag detection system
CA2657393A1 (en) 2006-04-21 2007-11-01 Berry Metal Company Metal making lance tip assembly
US8926895B2 (en) * 2008-01-24 2015-01-06 A.H. Tallman Bronze Company, Limited Post-combustion lance including an internal support assembly
DE102010034315A1 (de) * 2010-02-01 2011-08-04 SMS Siemag AG, 40237 Verfahren zur Überwachung einer metallurgischen Anlage und metallurgische Anlage
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CA3020361C (en) 2023-10-03
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US20190119765A1 (en) 2019-04-25
JP6953510B2 (ja) 2021-10-27
KR102330422B1 (ko) 2021-11-24
KR20180129835A (ko) 2018-12-05
WO2017178606A1 (fr) 2017-10-19
EP3443131A1 (de) 2019-02-20
PL3443131T3 (pl) 2020-09-21
US10858714B2 (en) 2020-12-08
JP2019513905A (ja) 2019-05-30
BE1023609B1 (fr) 2017-05-16

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